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Research Papers

Flow Boiling Heat Transfer on Micro Pin Fins Entrenched in a Microchannel

[+] Author and Article Information
Santosh Krishnamurthy, Yoav Peles

Department of Mechanical, Aerospace, and Nuclear Engineering, Rensselaer Polytechnic Institute, Troy, NY 12180

J. Heat Transfer 132(4), 041007 (Feb 19, 2010) (10 pages) doi:10.1115/1.4000878 History: Received November 24, 2008; Revised September 30, 2009; Published February 19, 2010; Online February 19, 2010

Flow boiling of 1-methoxyheptafluoropropane (HFE 7000) in 222μm hydraulic diameter channels containing a single row of 24 inline 100μm pin fins was studied for mass fluxes from 350kg/m2s to 827kg/m2s and wall heat fluxes from 10W/cm2 to 110W/cm2. Flow visualization revealed the existence of isolated bubbles, bubbles interacting, multiple flow, and annular flow. The observed flow patterns were mapped as a function of the boiling number and the normalized axial distance. The local heat transfer coefficient during subcooled boiling was measured and found to be considerably higher than the corresponding single-phase flow. Furthermore, a thermal performance evaluation comparison with a plain microchannel revealed that the presence of pin fins considerably enhanced the heat transfer coefficient.

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Copyright © 2010 by American Society of Mechanical Engineers
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Figures

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Figure 1

Device overview showing the device dimensions

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Figure 2

Images showing: (a) isolated bubble region (I), (b) bubble interacting (BI), (c) multiple flow region (M), and (d) annular flow (A)

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Figure 3

Flow maps based on wall heat flux for all the mass fluxes: (a) G=350 kg/m2 s, (b) G=564 kg/m2 s, (c) G=689 kg/m2 s, and (d) G=827 kg/m2 s

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Figure 4

Flow map showing the different flow patterns along the channel

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Figure 5

(a) The variation in single-phase heat transfer coefficient as a function of wall heat flux and (b) variation in Nusselt number as a function of the Reynolds number

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Figure 6

Heat transfer coefficients as a function of wall heat flux: (a) G=350 kg/m2 s, (b) G=564 kg/m2 s, (c) G=689 kg/m2 s, and (d) G=827 kg/m2 s

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Figure 7

The variation in heat transfer coefficient as a function of local quality (heat flux in W/cm2 in parenthesis)

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Figure 8

Comparison of convective resistance as a function of mass flow rate for both devices

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Figure 9

Enhancement in the single-phase Nusselt number for different Reynolds numbers

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Figure 10

Comparison of heat transfer coefficients for a microchannel with pin fins and a plain microchannel for different mass fluxes: (a) Gch=282 kg/m2 s, (b) Gch=345 kg/m2 s, and (c) Gch=413 kg/m2 s

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Figure 11

Comparison of thermal convective resistances for both devices: (a) Gch=282 kg/m2 s, (b) Gch=345 kg/m2 s, and (c) Gch=413 kg/m2 s

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Figure 12

Enhancement in the heat transfer coefficient for a microchannel with pin fins as a function of mass quality

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